CN101718200B - Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator - Google Patents
Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator Download PDFInfo
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- CN101718200B CN101718200B CN2009100447688A CN200910044768A CN101718200B CN 101718200 B CN101718200 B CN 101718200B CN 2009100447688 A CN2009100447688 A CN 2009100447688A CN 200910044768 A CN200910044768 A CN 200910044768A CN 101718200 B CN101718200 B CN 101718200B
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Abstract
The invention discloses a shield cutter rotary drive pressure adapting hydraulic control system of a proportional valve controlled energy accumulator. The system comprises a main hydraulic loop and a pressure adapting loop, wherein the main hydraulic loop consists of a motor, a constant power variable pump, a cartridge valve, a control cover plate, a proportional overflow valve, a one-way valve, an electro-hydraulic reversing valve, a proportional reversing valve, an energy accumulator, a quantitative motor and a speed reducer. The system judges the load characteristic when a cutter cuts a rock mass by detecting the system pressure through a pressure sensor, adjusts the proportional reversing valve according to the preset fuzzy adaptive PID control strategy and the change of a pressure signal, reasonably controls the opening direction, size and duration of the energy accumulator to absorb the load impact under different working conditions, and stores the impact energy reutilized for driving the cutter so as to effectively control the influences of system cavity enlargement and rigidity reduction because the energy accumulator is connected. By adopting the proportional valve controlled energy accumulator, the system can adapt the load impact caused by the complex stratum better, and has better energy conservation and reliability.
Description
Technical field
The present invention relates to fluid pressure actuator, the shield cutter rotary driving pressure that especially relates to a kind of proportional valve controlled energy accumulator adapts to hydraulic control system.
Background technique
The shield structure is the modernized tunnel construction complete sets of equipment that integrates mechanical, electrical, hydraulic pressure, sensing, information technology, have efficient, fast, characteristics such as high-quality, safety.Especially in the construction of long tunnel and city subterranean tunnel, to execution conditions, construction period, good with the combined influence adaptability of factor such as construction safety, can carry out tunnel piercing under the complex environment more, influence to surrounding environment especially urban environment is littler, can finish the driving task safer, quickly and efficiently.
The shield cutter rotary drive system is the core constituent element of shield structure, be used for tunneling process and provide suitable rotating speed and moment of torsion for cutterhead, guarantee that cutterhead can continue the rotary cutting rock in drive-in step, have that power is big, speed ratio greatly, the characteristics of variable power wide ranges.Traditional shield structure circular cutting disk drives hydraulic system and adopts closed system usually, has compactness, quality is little, commutation is steady, the transmission efficiency advantages of higher.But closed system also has and is difficult for heat radiation, and systemic contamination is difficult for discharging, and safeguards comparatively shortcomings such as difficulty.Especially in the face of complicated ground environment; cutterhead is starting usually; operation; and even be subjected to bigger impact in the processes such as the braking cutterhead is stuck; system can't adapt to this impact tempestuously preferably; comparatively general in the past solution is to adopt the relief valve overflow to carry out safety protection; so both can't avoid fully impacting; also can cause the too much overflow of pressure oil liquid and system effectiveness is reduced; temperature raises; cause the working environment of hydraulic system to become more abominable; maintenance cost and difficulty improve, and also can cause cutter or damage because the response of long frequent impact or relief valve is untimely under opposite extreme situations.
The proportional valve controlled energy accumulator oil hydraulic circuit can be differentiated the complex load of different geology by pressure transducer, regulate by predefined Fuzzy Adaptive PID Control strategy Comparative Examples directional control valve, reasonably control the opening direction of accumulator, size and endurance, absorb different load shocks effectively, thereby broken away from closed system in the past and in the driving environment of complex formation, tackled the impact damage that the complex load sudden change produces and the power loss of frequent overflow, and impact energy can be stored and utilization again, improved adaptability and the energy utilization ratio of shield cutter drive system to the stratum.
Summary of the invention
The object of the present invention is to provide a kind of shield cutter rotary driving pressure of proportional valve controlled energy accumulator to adapt to hydraulic control system, adopt the proportional valve controlled energy accumulator technology to realize that the shield cutter rotary of loaded self-adaptive drives hydraulic control system, system can detect the impact variation of load in real time, and controls the impact that the sudden change of accumulator absorbing load produces with this.
The technical solution adopted in the present invention is:
Motor in its major loop links to each other with permanent power and variable pump through coupling; The inlet port of permanent power and variable pump connects the oiler of oil suction oil purifier, links to each other with the high pressure filter inlet behind the oil outlet pressure gauge in parallel; The oil outlet of high pressure filter and the oiler that connects one-way valve after the oiler of cartridge valve is in parallel; The oiler of the safety valve that proportional pressure control valve and control cover plate are built-in links to each other with the control port of cartridge valve by control cover plate; The oil outlet of cartridge valve, safety valve and proportional pressure control valve links to each other with the oiler of oil return oil purifier, the oil outlet connected tank of oil return oil purifier; The P mouth of electro-hydraulic reversing valve links to each other with the oil outlet of one-way valve, the T mouth links to each other with fuel tank, link to each other with motor one side hydraulic fluid port after the oiler parallel connection of the P mouth of A mouth and proportional reversing valve, first pressure transducer, first relief valve, link to each other with motor opposite side hydraulic fluid port after the oiler parallel connection of the T mouth of B mouth and proportional reversing valve, second pressure transducer, second relief valve, control port is in parallel with the oiler of one-way valve; The A mouth of proportional reversing valve connects accumulator, and the B mouth blocks; First relief valve and second relief valve are built in motor, and oil outlet links to each other with fuel tank; The transmission shaft of motor links to each other with speed reducer.
The beneficial effect that the present invention has is:
1) adopts opening direction, size and the endurance of controlling accumulator based on the electric-hydraulic proportion under the Fuzzy Adaptive PID Control strategy, the access state of accumulator is adjusted in the variation that detects load in the shield driving process in real time according to the pressure transducer of high and low pressure side setting, the compression shock that brings of absorbing load sudden change effectively, the energy loss of avoiding the frequent overflow of system to produce, impact energy can also be stored again and utilize, improve the efficient and the reliability of system, thereby realized the pressure adaptive under the complicated geological environment.
2) adopt permanent power and variable pump control fixed displacement motor, replace throttle grverning with volumetric speed control, come the flow output size of control pump by the electrical signal of pressure transducer, thereby satisfy the different capacity demand under the different geological conditions, realize the power adaptive that cutter rotary is driven.To improve the efficient of system effectively, avoid a large amount of spill lossess.
3) adopt the keying of proportional pressure control valve control cartridge valve, the electrical signal size of the electromagnet by the preset proportion relief valve is controlled the moment of torsion of cutterhead under different operating modes, and can seamlessly transitted under the various operating modes between soft rock and the hard rock.
4) adopt open system, than closed system can dispel the heat better, maintenance system cleaning, safeguard also more simple.
5) at pump discharge one-way valve is set,, closes rapidly in the time of can greater impact occurring in system simultaneously, prevent that pump from being impacted for electro-hydraulic reversing valve provides the commutation pilot pressure.
Description of drawings
Fig. 1 is that the shield cutter rotary driving pressure of proportional valve controlled energy accumulator of the present invention adapts to the hydraulic control system structure principle chart.
The invention will be further described below in conjunction with drawings and Examples.
Embodiment
As shown in Figure 1, the motor 4 in its major loop of the present invention links to each other with permanent power and variable pump 6 through coupling 5; The inlet port of permanent power and variable pump 6 connects the oil outlet of oil suction oil purifier 2, and oil outlet pressure gauge in parallel 7 backs link to each other with the inlet of high pressure filter 8; High pressure filter 8 oil outlets and the oiler that connects one-way valve 13 after the oiler of cartridge valve 9 is in parallel; The oiler of the safety valve 11 that proportional pressure control valve 12 and control cover plate 10 are built-in links to each other by the control port of control cover plate 10 with cartridge valve 9; The oil outlet of cartridge valve 9, safety valve 11 and proportional pressure control valve 12 links to each other with the oiler of oil return oil purifier 1; The P1 mouth of electro-hydraulic reversing valve 14 links to each other with the oil outlet of one-way valve 13, the T1 mouth links to each other with fuel tank 3, link to each other with motor 19 1 side hydraulic fluid ports after the oiler parallel connection of the P2 mouth of A1 mouth and proportional reversing valve 15, first pressure transducer 17, first relief valve 20, link to each other with motor 19 opposite side hydraulic fluid ports after the oiler parallel connection of the T2 mouth of B1 mouth and proportional reversing valve 15, second pressure transducer 18, second relief valve 21, control port is in parallel with the oiler of one-way valve 13; The A2 mouth of proportional reversing valve 15 connects accumulator 16, and the B2 mouth blocks; First relief valve 20 and second relief valve 21 are built in motor 19, and oil outlet links to each other with fuel tank 3; The transmission shaft of motor 19 links to each other with speed reducer 22.
Working principle of the present invention is as follows:
When motor 4 electric startup, drive permanent power and variable pump 6 through coupling 5 and rotate, the inlet port of permanent power and variable pump 6 by oil suction oil purifier 2 from fuel tank 3 oil suctions.Pressure gauge 7 is used to detect the pressure of permanent power and variable pump 6 oil outlets.The fluid that permanent power and variable pump 6 is discharged filters the back through high pressure filter 8 and divides three the tunnel: the first via connects cartridge valve 9; by the built-in safety valve 11 of control cover plate 10 and the unlatchings of proportional pressure control valve 12 common control cartridge valves 9; 11 protective system safety effects of safety valve; proportional pressure control valve 12 can be set different cracking pressures according to concrete operating mode, plays the pressure limiting effect.When oil filter press 8 outlet pressures reach the cracking pressure of safety valve 11 or proportional pressure control valve 12, cartridge valve 9 is opened, and fluid directly overflows back fuel tank 3 by cartridge valve 9.The second the tunnel inserts the control port of electro-hydraulic reversing valve 14 before one-way valve 13 oilers, be used to control selector valve 14 commutations.Third Road enters the P1 mouth of electro-hydraulic reversing valve 14 by one-way valve 13, and one-way valve 13 provides the commutation pilot pressure for electro-hydraulic reversing valve 14, closes rapidly in the time of can greater impact occurring in system simultaneously, prevents that permanent power and variable pump 6 from being impacted.
All must not when electricity when electro-hydraulic reversing valve 14 left and right sides electromagnet, electro-hydraulic reversing valve 14 is operated in meta M type function, and A1, B1 mouth are closed, P1 mouth and the connection of T1 mouth, fluid directly flows back to fuel tank 3 by the P1 mouth by the T1 mouth.When electro-hydraulic reversing valve 14 left electromagnet get when electric, the P1 mouth of electro-hydraulic reversing valve 14 and A1 mouth are connected, and the B1 mouth is connected with the T1 mouth, and high pressure oil is divided into three the tunnel by the P1 mouth after the outflow of A1 mouth: the first via connects the P2 mouth of proportional reversing valve 15.The A2 mouth of proportional reversing valve 15 connects accumulator 16, and the B2 mouth blocks, and P2 mouth and T2 mouth connect the both sides oil circuit of motor 19 respectively.Proportional reversing valve 15 mainly by left and right sides electromagnet electricly control the left and right side oil circuits that accumulator 16 inserts motors 19 respectively, when the left and right side electromagnet all must not electricity, accumulator 16 is connecting system not.The input current or the voltage swing of the both sides electromagnet by control ratio selector valve 15, opening degree that can control ratio selector valve 15, thereby the flow of control accumulator 16 connecting systems.When the left electromagnet of proportional reversing valve 15 gets electricly, the P2 mouth of proportional reversing valve 15 and A2 mouth are connected, and accumulator 16 inserts the left side oil circuit of motors 19.When the right electromagnet of proportional reversing valve 15 gets electricly, the A2 mouth of proportional reversing valve 15 and T2 mouth are connected, and accumulator 16 inserts the right side oil circuit of motors 19.The second the tunnel connects the pressure that first pressure transducer, 17, the first pressure transducers 17 are used to detect motor 19 left side oil circuits.Third Road enters motor 19 from the left side hydraulic fluid port, and the motor 19 first built-in relief valves 20 insert in the ingress, left side, prevent that motor 19 left side oil circuit high pressure from causing damage to motor 19.The motor 19 second built-in relief valves 21 are parallel to motor 19 right side oil ports, prevent that motor 19 right side oil circuit high pressure from causing damage to motor 19.This moment motor 19 forward rotation, driving speed reducer 22 is just changeing, speed reducer 22 reduces the rotating speed of motor 19 to satisfy the speed demand of cutterhead with specific reduction speed ratio.The fluid that motor 19 is discharged is divided into three the tunnel after being flowed out by the right side hydraulic fluid port: the first via connects the pressure that second pressure transducer, 18, the second pressure transducers 18 are used to detect motor 19 right side oil circuits.First pressure transducer 17 and second pressure transducer 18 can be by detecting motor left and right sides oil circuit in real time, pressure signal is converted to electrical signal and compares, judge the high-pressure oil passage of motor 19, thereby draw the situation of change of load, and control permanent power and variable pump 6 and proportional reversing valve 15.The second the tunnel connects the T2 mouth of proportional reversing valve 15.Third Road connects the B1 mouth of electro-hydraulic reversing valve 14, flows back to fuel tank 3 by T1 mouth fluid.When electro-hydraulic reversing valve 14 right electromagnet get when electric, the P1 mouth of electro-hydraulic reversing valve 14 and B1 mouth are connected, A1 mouth T1 with mouthful connect, high pressure oil is divided into three the tunnel by the P1 mouth after the B1 mouth flows out: the first via connects the T2 mouth of proportional reversing valve 15.The second the tunnel connects second pressure transducer 18.Third Road enters motor 19 from the right side hydraulic fluid port, and the motor 19 second built-in relief valves 21 insert in the ingress, right side.The motor 19 first built-in relief valves 20 are parallel to motor 19 left side oil ports.This moment, motor 19 backward rotation drove speed reducer 22 counter-rotatings.The fluid that motor 19 is discharged is divided into three the tunnel after being flowed out by the left side hydraulic fluid port: the first via connects first pressure transducer 17.The second the tunnel connects the P2 mouth of proportional reversing valve 15.Third Road connects the A1 mouth of electro-hydraulic reversing valve 14, flows back to fuel tank 3 by T1 mouth fluid.
Claims (1)
1. proportional valve controlled energy accumulator driving shield cutterhead pressure adaptation hydraulic control system, it is characterized in that: the motor in its major loop (4) links to each other with permanent power and variable pump (6) through coupling (5); The inlet port of permanent power and variable pump (6) connects the oil outlet of oil suction oil purifier (2), and the oil outlet of permanent power and variable pump (6) pressure gauge in parallel (7) back links to each other with the inlet of high pressure filter (8); High pressure filter (8) oil outlet and the oiler that connects one-way valve (13) after the oiler of cartridge valve (9) is in parallel; The oiler of the safety valve (11) that proportional pressure control valve (12) and control cover plate (10) are built-in links to each other by the control port of control cover plate (10) with cartridge valve (9); The oil outlet of cartridge valve (9), safety valve (11) and proportional pressure control valve (12) links to each other with the oiler of oil return oil purifier (1), the oil outlet connected tank (3) of oil return oil purifier (1); The P1 mouth of electro-hydraulic reversing valve (14) links to each other with the oil outlet of one-way valve (13), the T1 mouth links to each other with fuel tank (3), link to each other with motor (19) one side hydraulic fluid ports after the oiler parallel connection of the P2 mouth of A1 mouth and proportional reversing valve (15), first pressure transducer (17), first relief valve (20), link to each other with motor (19) opposite side hydraulic fluid port after the oiler parallel connection of the T2 mouth of B1 mouth and proportional reversing valve (15), second pressure transducer (18), second relief valve (21), the control port of electro-hydraulic reversing valve (14) is in parallel with the oiler of one-way valve (13); The A2 mouth of proportional reversing valve (15) connects accumulator (16), and the B2 mouth blocks; First relief valve (20) is built in motor (19) with second relief valve (21), and first relief valve (20) links to each other with fuel tank (3) with the oil outlet of second relief valve (21); The transmission shaft of motor (19) links to each other with speed reducer (22).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100447688A CN101718200B (en) | 2009-11-18 | 2009-11-18 | Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100447688A CN101718200B (en) | 2009-11-18 | 2009-11-18 | Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator |
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| CN101718200A CN101718200A (en) | 2010-06-02 |
| CN101718200B true CN101718200B (en) | 2011-08-31 |
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| CN2009100447688A Expired - Fee Related CN101718200B (en) | 2009-11-18 | 2009-11-18 | Shield cutter rotary drive pressure adapting hydraulic control system of proportional valve controlled energy accumulator |
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Families Citing this family (7)
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| CN102650304A (en) * | 2012-05-29 | 2012-08-29 | 中南大学 | Hydraulic synchronous driving system for adjusting unbalanced load based on proportional valve controlled energy accumulator |
| CN102788063B (en) * | 2012-08-22 | 2015-08-05 | 上海中联重科桩工机械有限公司 | Hydraulic pressure installation and piling machinery |
| US9086081B2 (en) * | 2012-08-31 | 2015-07-21 | Caterpillar Inc. | Hydraulic control system having swing motor recovery |
| CN104329300B (en) * | 2014-10-31 | 2017-02-15 | 柳工无锡路面机械有限公司 | Energy recovery system and energy recovery method for road roller vibration wheel |
| CN108953258B (en) * | 2018-09-25 | 2024-02-02 | 中国重型机械研究院股份公司 | Efficient and energy-saving hose diaphragm pump four-cylinder reciprocating driving pump control hydraulic system |
| CN113843277A (en) * | 2020-06-28 | 2021-12-28 | 上海梅山钢铁股份有限公司 | Hot coil box coiling forming control device and control method |
| CN112065359B (en) * | 2020-09-21 | 2023-05-16 | 北京三一智造科技有限公司 | Drilling control method and rotary drilling rig |
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| JP2001311389A (en) * | 2000-05-01 | 2001-11-09 | Mitsubishi Heavy Ind Ltd | Control device for tunnel boring machine |
| JP3363135B2 (en) * | 2000-10-17 | 2003-01-08 | 石川島播磨重工業株式会社 | Direction correction device |
| CN1560482A (en) * | 2004-03-12 | 2005-01-05 | 浙江大学 | Hydraulic propelling system for mining tunnel driving machine controlled by ratio flow pressure |
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| JP3670983B2 (en) * | 2001-05-21 | 2005-07-13 | 石川島播磨重工業株式会社 | Direction correction device |
| JP2008045385A (en) * | 2006-08-21 | 2008-02-28 | Sanwa Kizai Co Ltd | Water-pressure feeder to water-pressure cylinder for compensation for buried-pipe propulsive-direction compensator |
| CN101225839A (en) * | 2008-01-09 | 2008-07-23 | 浙江大学 | Energy-saving type shield hydraulic pressure control system using hydraulic pressure transformer |
| CN101408107A (en) * | 2008-11-11 | 2009-04-15 | 浙江大学 | Energy-saving type shield propulsion hydraulic system by using zone control |
-
2009
- 2009-11-18 CN CN2009100447688A patent/CN101718200B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001311389A (en) * | 2000-05-01 | 2001-11-09 | Mitsubishi Heavy Ind Ltd | Control device for tunnel boring machine |
| JP3363135B2 (en) * | 2000-10-17 | 2003-01-08 | 石川島播磨重工業株式会社 | Direction correction device |
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| CN1560482A (en) * | 2004-03-12 | 2005-01-05 | 浙江大学 | Hydraulic propelling system for mining tunnel driving machine controlled by ratio flow pressure |
| CN1587644A (en) * | 2004-07-09 | 2005-03-02 | 浙江大学 | Full power self adaptive shield cutter disc driving electrohydraulic control system |
| JP2008045385A (en) * | 2006-08-21 | 2008-02-28 | Sanwa Kizai Co Ltd | Water-pressure feeder to water-pressure cylinder for compensation for buried-pipe propulsive-direction compensator |
| CN101225839A (en) * | 2008-01-09 | 2008-07-23 | 浙江大学 | Energy-saving type shield hydraulic pressure control system using hydraulic pressure transformer |
| CN101408107A (en) * | 2008-11-11 | 2009-04-15 | 浙江大学 | Energy-saving type shield propulsion hydraulic system by using zone control |
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| CN101718200A (en) | 2010-06-02 |
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Granted publication date: 20110831 Termination date: 20131118 |